Ball reconditioner



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BALL lREGONDIIIIONER l() Sheets-Sheet lO Filed March ll, 1964 v United States Patent O 3,289,354 BALL RECONDITIONER Eric S. Stevens, St. Charles, Mo., and Otto E. F. Puhlmann, Muskegon, Mich., assignors to Brunswick Corporation, a corporation of Delaware Filed Mar. 11, 1964, Ser. No. 350,983 23 Claims. (Cl. 51-5) This invention relates in general to reconditioning apparatus, and more particularly to apparatus for reconditioning the outer surface of a bowling ball or the like.

Those familiar with the game of bowling are aware that as a ball is rolled down a bowling lane, dirt, grit, and other foreign particles have a :tendency to accumulate on the outer surface of the bowling ball, and mar its appearance, as well as change the effect of spin deliberately imparted to the ball. It is well known in the prior art to provide means for polishing the outer surface of a bowling ball so that the ball is relatively clean and is provided with a lustrous exterior. Known bowling ball polishing machines have proven unsatisfactory in that they have not been capable of removing nicks, gouges, and scratches from the exterior of a bowling ball, which are commonly formed upon contact with particles on the bowling lane surface, and with the bowling pins; and also by the ball return mechanisms utilized in present day bowling establishments.

Accordingly, one of the general purposes of the present invention is to provide a ball reconditioning machine which will remove a predetermined amount of material from the outer surface of a bowling ball, so as to remove undesirable indentations from the outer surface of the ball.

lt is also known to those skilled in the art to provide apparatus for grinding the outer surface of spherical objects. Such known devices have been unsatisfactory for use with bowling balls for several reasons. For example, many devices have not been capable of removing a uniform amount of material from the` entire outer surface of a bowling ball, and therefore have been unsatisfactory because only precision grinding will retain the perfectly spherical shape that is required for a bowling ball. Other devices have either removed too much or too little material from the outer diameter and have not been susceptible of close control throughout the desired grinding operation. Also, prior art grinding devices are typied by a long grinding cycle which renders them undesirable for a commercial bowling establishment.

One of the more serious drawbacks of prior art grinding machines is that it has been necessary to completely remove the ball from the grinding machine after the grinding operation, and physically transfer it to a polishing machine wherein the grinding marks are removed and the ball is polished to a lustrous finish. This provides an nndesirably lengthy delay, and makes it necessary for anyone who wishes to completely recondition a bowling ball to have a multitude of equipment.

Therefore, another general object of the present invention is to provide a single machine wherein a bowling ball may be completely reconditioned in stages akin to production techniques.

An object of the present invention is to provide a ball reconditioning machine with means for grinding the outer surface of a bowling ball to remove irregularities therefrom, a rst polishing means to remove grinding marks and provide a clean polished surface, and a second polishing means for providing a lustrous exterior on the ball.

Another object of the invention is to provide a ball reconditioning machine as set forth in the preceding paragraph wherein the ball is rotatably supported at a working position, and the grinding means, and rst and second 3,289,354 Patented Dec. 6, 1966 Ice polishing means are sequentially moved into operative engagement with the bowling ball.

A further object of the invention is to provide timing means for a ball reconditioner as set forth above, wherein the timing means automatically controls the length of the grinding and first and second polishing cycles, and wherein the grinding cycle may be bypassed, if desired.

Still another object is to provide a ball reconditioner, as described above, with means for automatically dressing the grinding wheel so that a consistent amount of stock will be continuously removed from the balls being ground.

A still further object of the invention is to provide a ball reconditioner, as described above, with means for applying polishing compound to both the first and second polishing means so that the desired polishing of the balls will be effected.

These and other objects of the invention will hereinafter become more fully apparent from an examination of the following specification taken in connection with the annexed drawings, wherein:

FIG. l is a front perspective view taken from one side of a preferred embodiment of the invention;

FIG. 2 is a front perspective view similar to FIG. 1 but taken from the opposite side of the machine;

FIG. 3 is a fragmentary front perspective view taken from the same side as FIG. l, but at a different angle, and showing certain elements of the invention in greater detail;

FIG. 4 is a side elevational view on an enlarged scale showing the turret assembly and the means for indexing the turret;

FIG. 5 is a sectional View taken generally along line 5-5 of FIG. 4, with certain parts broken away for clarity;

FIG. 6 is a side elevational view on an enlarged scale of the ball holding means of the present invention;

FIG. 7 is a front elevational view of the apparatus illustrated in FIG. 6;

FIG. 8 is a plan view of the drive and timing apparatus of the present invention;

FIG. 9 is an enlarged side elevational view of the apparatus illustrated in FIG. 8 with certain parts broken away for clarity;

FIG. l0 is a sectional view taken generally along line 1li-10 of FIG. 9;

FIG. ll is a side elevational view of the dressing device of the present invention, shown in somewhat diagrammatic form, and with certain parts broken away for' clarity;

FIG. 12 is a front elevational view of the apparatus set forth in FIG. 1l;

FIG. 13 is a plan viewl of the structure illustrated in FIG. l1 and FIG. 12; and

FIG. 14 is a side elevational view of the buillng compound applicator of the present invention.

While this invention, is susceptible of embodiment in many different forms, there is shown in the drawings and will herein be described in detail one specific embodiment, with the understanding that the present disclosure is to be considered as an exemplitcation of the principles of the invention and is not intended to limit the invention to the embodiment illustrated. The scope of the invention will be pointed out in the appended claims.

General organization Referring now to the drawings, wherein like reference characters designate like or corresponding parts through- 4out the several views, the illustrated embodiment of the 22 and 23 positioned at the rear and at the central portion of element 21 respectively, and `a rearwardly inclined front element 24 positioned at the forward end of element 21. Front element 24 is connected to vertical element 23 by a generally horizontally disposed central portion 25 which includes a portion 26 extending generally vertically upwardly from the rearward end of portion 25. A generally horizontally disposed element 27 connects the upper ends of elements 22 and 23, and a generally forwardly inclined element 28 extends from the upper portion of element 22 and is secured to the upper part of portion 26. Frame member 30 includes a generally horizontally disposed lower element 31 having a generally vertically extending element 32 positioned at the rearward end thereof, and a generally rearwardly inclined element 33 positioned at the forward end thereof. Front frame element 33 includes a generally horizontally disposed central portion 34 that is positioned generally opposite frame portion 25, and a generally vertically extending portion 35 extending upwardly from the rearward end of portion 34. A forwardly inclined element 36 is connected between the central portion of element 32 and the rearward end of portion 34, and element 32 includes a forwardly inclined upper portion 37 that is con nected to the upper portion of element 35. A transverse element 29 connects the upper portion of elements 26, 28, 35, and 37, while transverse elements 38 and 39 connect elements 22 and 32, and 24 and 33, respectively. Suitable casters 40 support the aforedescribed frame structure, so that the ball reconditioner may be moved as desired.

A ball holding cradle is pivotally mounted on the main frame of the ball reconditioner by a pair of suitable supports 41 and 42 that are provided on frame element 39. Ball cradle 50 includes a pair of spaced, generally identically shaped side frame members 52 and 53, each having upwardly diverging sides 54 and 55 connected together at their bottom portions, connected at their mid portions by horizontal member 56, and connected at their upper portions by horizontal member 57. The lower portion of members 52 and 53 are journalled in supports 41 and 42 as at 58, and suitable bearings may be provided as at 59 (FIG. 6 and FIG. 7) if desired.

A transverse member 60 spans the upper ends of forward cradle elements 55, and is provided with a pair of spaced upwardly extending lugs 61 and 62 which rotatably support a roller 63 therebetween. A pair of spaced upstanding lugs 64 and 65 are provided on the upper surface of the transverse member 57 of each cradle frame member 52 and 53, with rollers 66 being rotatably supported between lugs 64 and 65. A suitable ball rotating member 67 extends transversely between ball cradle frame members 52 and 53, and is secured to a shaft 67a that is rotatably supported in a hub 68, and which is driven through pulley 69 (see FIG. 7). Rollers 63 and 66, and ball rotating member 67 together collectively define a ball working station. The outer surface of ball rotating member 67 may be provided with an elastomeric material to enhance the gripping ability with the ball being reconditioned so that relative motion between the ball and Work wheel is obtained.

Means are provided for periodically twisting the ball, so that the exterior of the ball will be uniformly worked. The ball twisting means includes a sector 70 (best seen in FIG. 7) that is secured to an arm 71 which is rotatably supported in a hub 72 carried by a transversely extending frame member 73. Arm 71 is rotated by pulley 74 which is driven by belt 75. Belt 75 is trained over a driving pulley 76 and engages an idler pulley 77 that is carried by a depending arm 78 biased toward belt 75 by spring 78a. A strip of elastomeric material 80 is provided on sector 70 so that as sector 70 rotates, strip 80 will engage the undersurface of the ball B and twist it a predetermined amount to insure that its outer surface will be uniformly worked.

Means are provided for lifting the ball B out of the working position at the end of the reconditioning cycle,

and comprise a pair of generally horizontal, rearwardly extending arms 81 and 82 spanned at their rearward end by a transverse member S3 (best seen in FIGS. 6 and 7). The forward ends of arms 81 and 82 are secured to a transverse shaft 84 that is rotatably mounted in cradle frame members 55 to pivot arms 81 and 82 upwardly to lift the ball B from the working station. Shaft 84 is pivoted by `a link 85 fixed thereto which is actuated by a rod 86 responsive to appropriate movement in the turret assembly to be hereafter described.

A turret assembly, indicated generally at 90 in FIG. 4, is indexably mounted on the main frame of the ball reconditioning machine for sequential movement of each of the ball working members into a position adjacent the ball working station defined at the upper portion of the ball carrying cradle. Turret assembly 90* includes a grinding wheel 91, a first buliing wheel 92 (for cut bufling), and a second buing wheel 93 (for finish buffing). It will be understood that in the illustrated embodiment, grinding wheel 91 will remove a predetermined amount of stock from the outer periphery of the ball being reconditioned, and first butiing wheel 92 will perform a rough buiing operation, while second buffing wheel 93 will perform a polishing operation. It should be further understood, of course, that more than one grinding wheel may be provided, if desired, and also more or less buffing wheels may be provided. In any event, timing means to be hereafter described, are provided to regulate the length of the grinding and polishing cycles, and also to bypass the grinding cycle, if desired.

A turret assembly 90 is fixed to a shaft 95 that extends transversely across the main frame, and which has its end portions rotatably mounted in aligned bearings in brackets 96 and 97, which are provided on frame portions 25 and 34, respectively. Turret assembly 90 includes a body 98 fixed to shaft 95, as by key 99. Body 93 is provided with pairs of transversely aligned, radially outwardly extending arms 100 between which the ball working wheels are mounted. The mounting for each of the ball working wheels is substantially identical, so that only one is shown in detail (FIG. 5). A stationary shaft 101 extends transversely between the end portions of arms 100, and is secured thereto by end caps 102 that are bolted to the ends of arms 100 (FIG. 4). A spool 103, upon which the ball working wheel is fixed, is rotatably mounted on shaft 101 as by bearings 104. A pulley 105 is keyed to spool 103 for rotation thereof by a belt drive means to be hereafter described.

The means for indexing the turret assembly 90 (portions of which can be seen in FIGS. 2, 4, 5, 6, and 8) includes a sprocket driving a second sprocket 112 by a chain 111. Sprocket 112 is rotatably mounted on a support member 113 carried by a ange depending from frame portion 34. A cam 115 is secured to sprocket 112 for rotation therewith, and engages a suitable roller 116e carried on an arm 116 which extends outwardly and rearwardly from the rearward end of ball cradle member 57. It will be readily understood that as the enlarged portion of cam 115 rotates into engagement with the roller 116e, the ball cradle 50 will be pivoted forwardly away from the main frame of the ball reconditioner. A spring 117 (FIG. 2), or its equivalent, such as shock absorber 117a (FIG. 6 and FIG. 7) is connected between the end portion of shaft 84 and a bracket 118 mounted on frame element 33 to return the ball cradle 50 to a position adjacent the main frame after the enlarged portion of cam 115 has rotated past the roller 116a. Cam 115 carries a crank pin 119 which is adapted to drive a Geneva mechanism 120 that is used to index the turret assembly 90. As is best seen in FIG. 4, Geneva mechanism 120 includes six steps defined by radially extending slots 121. The Geneva mechanism of the illustrated embodiment is provided with six steps in order to provide an intermediate step or position between each pair of ball working wheels.

As is best seen in FIG. 4 and FIG. 5, a cam 122 is fixed to Geneva mechanism 120, and both are keyed to shaft 95 by the aforementioned key 99. An arm 123 is secured at its upper end .to a transverse pin 124 carried by a bracket 125 that depends from frame element 29 (FIG. 2). Arm 123 is pivotally secured at its lower end to the rearward end of rod 86. A roller 126 is provided at the intermediate portion of arm 123, and is engageable with the enlarged portion of cam 122, as is best seen in FIG. 4, to actuate the ball lift arms 81 and 82.

Each of the radial arms 100 of the turret assembly include a stop 100a that is engageable with a roller 130a carried by an upwardly and rearwardly extending arm 130 mounted on the rearward portion of the ball cradle 50 (see FIG. 6) when the turret is indexed to one of the steps intermediate the working Wheels. Thus, in any of the intermediate positions of the turret assembly, the ball cradle 50 will be held in a forward position by the engagement of roller 13061 with stop 100:1, and cam 115 will rotate without engaging roller 116a.

The means for rotatably driving the single working wheel in the ball working position includes a driven pulley 135 which is xed to the output shaft of a drive motor M (FIG. 2). A belt 136 is trained over the large diameter of pulley 135 and extends upwardly to an idler pulley 137 that is rotatably supported in `the frame member 29. Belt 136 then extends forwardly where it is trained over the pulley 105 on the ball working member in the ball working position. The location of pulleys 135 and 137 is such that only the pulley of the ball working wheel adjacent the ball cradle 50 comes in contact with and is driven by belt 136. As each ball working Wheel is indexed into the ball working position, its pulley 105 engages belt 136, While the pulley 105 connected to the ball working member leaving the ball working position moves out of contact with belt 136.

The timing means for controlling the operation of the ball reconditioning machine are mounted in a gear box 142 that is suitably secured to the front transverse element 39 of the main ball reconditioner frame and will be best understood from a consideration of FIG. S-FIG. 10. This timing device is driven by motor M by means of belt 133 which is trained over pulley 132 on the timer and hub 134 of the motor M pulley 135. A worm gear, not shown, is provided at the inner end of a shaft 143 to which pulley 132 is afxed, with the worm gear driving a gear 144 on a transverse shaft 145. The rearward end of shaft 145 is provided with a worm gear, not shown, that drives another gear 146 carried by a shaft 147 extending transversely with respect to shaft 145. A sprocket 148 is secured to shaft 147, and drives the bufng compound applicator and the grinding wheel dresser to be hereafter described. Pulley 76, which drives the ball twisting device, described above, is secured to the forwardly extending end of shaft 145. The right hand end of shaft 147, as viewed in FIG. 8, carries the sprocket 110 which drives the above described turret assembly indexing means.

As is best seen in FIG. 10, shaft 147 is rotatably supported in a transversely extending gear box member 148a as by bearings 149. An adapter 150 is secured to transverse member 148a by bolts 151, only one of which is shown, with the bore and adapter 150 being spaced from shaft 147 so that the shaft is free to rotate relative thereto. A stationary gear 152, comprising part of a planetary type gear reducer, is positioned in spaced relation with respect to shaft 147, and is fixed to adapter 150 as by set screws 153, only one of which is shown. An arm 154 is xed to shaft 147 for rotation therewith by a key 155, and a pair of gears 157 and 158 are provided on opposite sides at the outer end of arm 154. A gear support member `159 is rotatably mounted in the end of arm 154 by a bushing 160 with gears 157 and 158 iixedly secured to the support member by screws 161 and 162 for rotation together. Another gear 163 is mounted on a bushing 164 for rotation relative tto shaft 147, and is driven by gear 158. Each of gears 152, 157, 158 and 163 have the same pitch diameter, with gears 152, 157 and 158 each having the same number of teeth, and with gear 163 specially designed to properly interact with gear 158 while having a lesser number of teeth, preferably one less tooth :than gear 158. Each of gears 152, 157, 158 and 163 preferably have a large number of teeth, so that a predetermined slow rotational movement will be imparted to gear 163 relative to shaft 147 as a result of the planetary gear reducer interposed therebetween. A cam 165 is fixed to gear 163 for rotation therewith, and is adapted to trigger a one revolution clutch to be hereafter described to rotate shaft 166, to which the turret index drive pulley 110 is xed.

As is best seen in FIG. 9, cam 165 is divided into two substantially identical 180 portions, each of which is provided with a plurality of notches. Each of notches 167, 168, 169, and correspond to indexing positions, while land areas 171 and 172 correspond to the first and second bufling positions, as will hereinafter become more fully apparent.

A cam follower 175 is pivotally mounted on a cam follower arm 177 at 176, and is adapted to ride along the outer periphery of cam 165. Arm 177 is pivotally i mounted on a transverse shaft 180, with a link 181 being fixed to arm 177 for pivotal movement therewith. A spring 178 is connected between the upper end portion of follower 175 and link 181 to urge the follower 175 against a suitable stop 179 carried by arm 177. A spring Y 182 is connected between the frame 142 and the upper end portion of link 181 to bias the follower arm 177 toward cam 165. A second arm 184 is pivotally mounted on shaft 180, and extends in substantially an opposite direction from arm 177. Arm 184 includes a latching surface 185 which is engageable with the latching surface of a clutch pawl to be hereafter described. A transverse pin 186 is carried by the lower portion of link 181 for movement of the arm 184 into and out of latching engagement with the clutch pawl. A suitable spring 183 is biased between the frame 142 and a socket formed in the upper surface of arm 184 to urge arm 184 toward the clutch pawl.

A latch 187 is pivotally mounted on frame 142 as at 188, and is provided with a notched portion 189 that is engageable with an extension 177a on arm 177 to hold the cam follower 175 out of engagement with the outer periphery of cam 165. Pivotal movement of latch 187 may be effected by solenoid means, not shown, that are secured to the end of latch 187 as at 190.

A toothed clutch input member 192 is fixed to shaft 147 for rotation therewith by a key 193. A plate 194 (best seen in FIG. l0) is seated within a recess in clutch input member 192, and is xed to shaft 147 by a bolt 195 to retain input member 192 against axial movement relative to shaft 147. A clutch pawl 196 is pivotally secured, as at 197, to a clutch output member 198, with which shaft 166 is integrally formed. Pawl 196 includes a latching surface 199 that is engageable with the latching surface 185 of arm 184, and a tooth 200 that is engageable with the teeth on input member 192. Pawl 196 is urged toward engagement with clutch member 192 by means of spring 1960.

Means are provided for releasing latch 187 from engagement with arm 177, and comprises a pair of levers 202 pivotally secured to cam 165 at 180 opposed positions7 as at 203. The end portion 187a of lever 187 is positioned in the path of travel of the end portions 204 of levers 202, so that as cam 165 rotates, the end portions 204 will engage the portion 187a` and pivot lever 187 to free arm 177 for movement relative to cam 1,65.`

7 Levers 202 are held against stops 286 that are carried by cam 165 by springs 287 that are connected between posts carried by the levers 282 and by the cam 165.

Operation As mentioned above, the ball reconditioning machine of the present invention is adapted to be used in cornmercial bowling establishments. Often it will be desirable to bypass the grinding operation of the reconditioning machine, and merely utilize the two buffxng stages as for example when a ball is merely soiled. To this end, a selector switch, not shown, on a coin mechanism, not shown, which is utilized to actuate the machine, may be energized upon the depositing of an appropriate coin to select either a short cycle or a long cycle. The short cycle, which excludes the grinding operation, will be firstly described.

The machine will initially be in the load-unload position, that is, with the turret positioned so that the intermediate step between the grinding wheel and the second buffing wheel is positioned adjacent the ball working station. It will be understood, that in this position the motor is not actuated so that none of the movable parts are moving. A ball is then placed in the ball working station on top of the ball cradle 50 so as to rest against guide rollers 63 and 66, and drive member 67. A suitable enclosure, not shown, is then placed over the exposed machine parts, and the motor is actuated by inserting an appropriate coin. The motor M drives the input pulley 132 to the timing device through the belt 133, and cam 165 is rotated by the interaction of shafts 143, 145, and 147, and through gears 144, 146, 152, 157, 158, and 163. The motor speed, pulley sizes, and number of gear teeth are selected so that the cam 165 rotates at a relatively slow speed, as for example, once in every five minutes. Notches 167 correspond to the load-unload position, so that as cam 165 begins to rotate in the counterclockwise direction, as viewed in FIG. 9, the follower 175 will ride up to and along the outer periphery of cam 165, and move from notch 167 to notch 168. When follower 175 drops into notch 168, arm 177 will pivot relative to shaft 188, and the transverse pin 186 on link 181 will contact the undersurface of arm 184 to pivot latching surface 185 out of engagement with the latching surface 199 of the clutch pawl 196. Spring 19661 will then pivot clutch pawl 196 around pin 197 so that the tooth 208 will engage the adjacent tooth on the clutch input member 192 causing it to rotate therewith. The clutch output member 198 will travel one revolution with the clutch pawl 196 to impart one revolution to the input sprocket 118 of the turret indexing drive, to be more fully explained later. Rotation of sprocket 118 will drive chain 111 to rotate the sprocket 112 and the cam 115 aixed thereto. The enlarged portion of cam 115 will engage the roller 116a on arm 116 and pivot the ball cradle relative to the main frame of the machine, so that the turret assembly has sufficient clearance to index. Crank pin 119 willthen enter the appropriate slot 121 in the Geneva mechanism 120, and the turret will be indexed 60 to position the grinding wheel adjacent the ball. Simultaneously with the indexing of the turret, springs 117 will return the ball cradle to working position adjacent the main frame.

Immediately after the aforedescribed sequence has taken place, follower 175 will drop into notch 169, it being understood that cam 165 rotates considerably more slowly than input member 192. It will be noted that notches 169 are substantially larger than notches 168, and in fact, notches 169 are sized so that the clutch pawl 196 will make two revolutions with the clutch input member 192. This Will cause the turret assembly to index twice, first from the grinding wheel to the position intermediate the grinding wheel and the first butlng wheel, and second to the first buffing. When the turrent is in the intermediate position, the roller 13M will be resting on stop 18851 to hold the ball cradle in a forward position. As the turret indexes the grinding wheel into its working position, the spring 117 returns the cradle 50 to the ball working station. When the cam follower 175 reaches the end of notch 169, and rides up on the land area 171, the latching surface 185 will engage the clutch pawl latching surface 199 and the clutch pawl will be disengaged from the clutch input member 192. The cam follower 175 will then ride up on the land area 171 during the rst buffng cycle during which time the belt 136, that is driven by the pulley fixed to the motor output shaft, drives the pulley 185 associated with the first buffing wheel 92. cycles, the ball is continuously rotated by member 67, and periodically twisted by member 88, so that the outer periphery of the ball will be uniformly worked. When the follower 175 reaches the end of the land area 171, it drops into the notch 170, which corresponds in length to notch 169, and the turret will again be indexed twice to bring the second or finishing buffing wheel into working position. Prior to the indexing of the first butfing wheel away from the working position, cam 115 engages roller 116er to pivot the cradle 58 to a forward position, so that the turret is free to index. After the second bung wheel is in working position, the cam follower 175 will ride up on the land area 172 until the second bufiing operation is completed, `when it will then drop `into notch 167 and index the turret to the position intermediate the second buffing wheel and the grinding wheel. As the turret indexes to the position intermediate the second buffing wheel and the grinding wheel, the enlarged portion of cam 122 engages the roller 126 on arm 123 to actuate the ball lifting arms 81 and 82 through rod 86 and link 85. A selector switch, not shown, will then deenergize the motor, and the movable parts will then come to rest so that the ball may be removed from the ball holding cradle. Thus, it will be understood that in the short cycle, one-half of cam is used, and that if the cam 165 rotates once in 5 minutes, the du-ration of the first and second buffing operations will be 21/2 minutes.

When it is desired to use the long cycle, including the grinding operation, a coin (larger in domination than that used in connection with the short cycle) is inserted in the coin mechanism, and a solenoid, not shown, is actuated to urge latch 187 in a counterclockwise direction. Thus, when follower drops into notch 168 to index the grinding wheel into the ball working position, and immediately thereafter when it rides up the higher land area 171a between notches 168 and 169, the follower arm 177 will be lifted high enough so that the groove 189 of the latch 187 will grip the extension 177m of follower arm 177 to prevent it from dropping into the notch 169. The solenoid which pivoted latch 187 is now deenergized but the follower arm 177 will be held up by notch 189 until lever 187 is disengaged by lever 282. The follower 175 will be prevented from dropping into any of the notches in the cam periphery by the lever 187 for approximately 180 revolution of cam 165, when the end portion 187:1 of latch 187 will engage the end portion 204 of release lever 262. When latch 187 engages release member 282, latch 187 will be pivoted about pivot 188 away from the follower arm 177 to free the follower 175 for movement into the cam notch 169. When the cam follower 175 drops into the notch 169, the butiing operation described above `in connection with the short cycle is then carried out in its entirety. Thus, it will be apparent that in the long cycle, when cam 165 rotates once in 5 minutes, the duration of the long cycle will be 5 minutes.

Grinding wheel dresser During the grinding operation, the grinding wheel will have a tendency to become loaded with some of the material it has removed from the ball. To keep this ma- During each of the ball working' terial or these grindings from building up upon the grinding wheel, and to maintain a true arcuate grinding surface, the present invention provides the dressing device to be presently described.

Referring now to FIG. 11-FIG. 13, the dressing device includes an actuating lever 210 pivotally secured adjacent its mid-point as at 211, to the arm 100 of the turret assembly which leads to the rst bufng wheel 92. The lever 210 includes a rst cam follower 212 at the left hand end thereof, as viewed in FIG. 11, that is adapted to engage the outer periphery of a stationary cam 213 lthat is secured to the radially outwardly extending arms 96a of bracket 96. Lever 210 includes a second cam follower 214 positioned between follower 212 and pivot 211, which is adapted to ride upon the outer periphery of a constantly rotating cam 215. Cam 215 is mounted for rotation about pivot 216, and is rotated by a sprocket 217 that is driven by sprocket 148 and chain 218 (FIG. 1). The sizes of sprockets 217 and 148 are selected so that the cam 215 has a relatively slow rotational speed, as for example three revolutions per minute. As will hereinafter become more fully apparent, this enables the dressing device to make the desired number of passes across the grinding Wheel during the dressing operation.

A ange 220 of generally L-shaped cross section is secured to the right hand end of lever 210, as viewed in FIG. 13, and defines spaced apart walls 221 and 222 between which the lower end of a link 223 is mounted for generally universal movement. The upper end of link 223 is connected for generally universal movement to one corner of a generally triangularly shaped bell-crank or lever 224, which is formed by spaced plates 226 and 227. As viewed in FIG. 12, the lower corner of triangular lever 224 is pivotally secured to a bracket 240 to be hereafter described by a bolt 230. Thus, when follower 214 rides over the rise portion of cam 215, lever 210 will be pivoted clockwise, as viewed in FIG. 11, and link 223 will swing outwardly to the left, as viewed in FIG. 12, to the position indicated at 223a, since the lower portions of link 223 move downwardly in that figure with lever 224 pivoting around bolt 230. Movement of the link 223 to the position shown at 223a will swing the dressing tool, to be hereafter described, across the surface of the grinding wheel 91.

The above mentioned bracket 240 includes a generally rearwardly and upwardly inclined portion 241 to -which lever 224 is pivotally secured, and a generally outwardly extending lower portion 242. A generally transversely extending member 243 is secured adjacent the lower portion of bracket portion 241, and extends outwardly above the grinding wheel 91. Transverse member 243 includes a side portion 244 terminating at its rearward end in a bifurcated lug 245 (see FIG. 13) that is pivotally mounted on transverse pin 211. A grinding wheel dressing tool 246 is mounted for pivotal movement on a sector shaped member 247 as at 248. The sector shaped member 247 consists of two generally identically shaped plates held in spaced relation by spaced bolts 249 which are secured to bracket portion 243. Pivotal movement of tool 246 is effected by a link 250 which is connected at one end to the upper right hand corner of lever 224, as viewed in FIG. 12, and at the other end to the central portion of tool 246. It will be understood, of course, that tool 246 is provided with a suitable slot to accommodate link 250. A dressing member 251, such as a diamond or the like, is fixed in the end portion of tool 246, and is adapted to engage the radial surface of grinding wheel 91 as tool 246 sweeps thereacross. A spring 253 is connected between an extension 245 of bracket 240, and the end cap 102 on the radial arm of grinding wheel 91, to bias the dressing tool 246 toward the grinding wheel. Another spring `254 is connected at one end to lever 210 between followers 212 and 214, and at the other end to the end cap 102 on the radial arm leading to second mufling wheel 93, to urge the followers 212 and 214 toward engagement with cams 213 and 215, respectively.

Means are provided for feeding the dressing tool 246 toward the grinding wheel 93 to compensate for wear of the grinding wheel during the grinding operation. To this end, an internally threaded socket 260 is fxedly mounted on the arm that leads to the grinding wheel 91. The lower end of a feed screw 261 is threadably received in socket 260, and as the feed screw is threaded into the socket, the bracket 240' will be pulled downwardly therewith, as viewed in FIG. 11, and the dressing tool 246 will be advanced into the grinding wheel.

A link 262 is mounted for pivotal movement on feed screw 261 beneath shelf portion 242, and is urged to a set position against a stop 263 carried by shelf portion 242 by a spring 264. A pawl 265 is pivotally mounted on the upper surface of link 262, and is engageable with the teeth of a ratchet section 266 which is integrally formed with feed screw 261. Thus, as link 262 pivots relative to the feed screw 261, pawl 265 will engage the teeth upon ratchet section 266 to feed screw 261 downwardly into socket 260, and under the urging of spring 253, the dressing tool 246 will be advanced into the grinding wheel 91. An outwardly extending pin 267 is carried by the downwardly bent outer end of link 262, and is periodically engageable with the inclined portion 271 of lever 270 to effect the pivotal movement of link 262.

Lever 270 is mounted adjacent its mid-point as at 272 for pivotal movement into and out of the position indicated in broken lines at 270a. Pivotal movement of lever 270 is effected by a solenoid 273 connected to lever 270 through a link 274. A spring 275 is connected to the lower end of lever 270 to urge the lever into the position indicated at 270a. When the lever is in the position shown at 270a, the inclined portion 271 is positioned in the path of travel of pin 267, so that the feeding of the grinding wheel dressing tool will be eifectedl as the turrent indexes.

It will be understood, of course, that when the short cycle described above is used, which consists of the first and second buffing operations, it will not be necessary, and in fact, it will be undesirable to dress the grinding wheel. To this end, the solenoid 273 is retracted to the solid line position shown in FIG. 11 upon the depositing of the appropriate coin in the `coin mechanism for the short cycle. The retraction of solenoid 273 causes the inclined portion 271 to be moved into the solid line position shown in FIG. 11, and thus out of the path of pin 267 so that no feeding of the grinding wheel dressing tool 246 will take place during the indexing of the turret. Lever 270 is provided with a catch portion 276 that is engageable with the follower 212 on lever 210 when the solenoid 273 is actuated, as is shown at 21251 in FIG. 11, and thus the swinging of the wheel dressing tool 246 is also effectively prevented during the short reconditioning cycle.

When the long cycle is used, including the grinding operation, it is necessary to dress the grinding wheel. However, it is desirable that the number of passes which the tool 246 makes across the Wheel 91 be kept to a minimum, so as not to needlessly wear out the grinding wheel. Thus, as the turret indexes, follower 212 will ride up upon the rise portion of cam 213, and follower 214 will be held out of engagement with cam 215 to prevent the pivoting of tool 246. When the turret is indexed to the position shown in FIG. 11, the follower 212 rides into the depression in cam 213, and follower 214 is in position for engagement with cam 215.

A vacuum device A is mounted on the main machine frame, and includes a hose H which extends upwardly to a position adjacent the ball working station, and is adapted to collect the particles ground from the ball.

Bung compound applicator In 4connection with the rough buing operation which 1s utilized to remove the grinding marks from the outer l l surface of the ball, and in connection with the nished buing operation which is used to provide a highly polished surface on the ball, it is desirable to periodically apply a small amount of appropriate polishing compound to the buffing wheel during the bufling operation. Since the bung wheels are rotating at a high rate of speed, and since only a very small amount of compound is needed, the mechanism for applying the buffing compound to the bung wheels is so constructed and arranged that the buing compound will contact the bufiing wheels for only an instant. While from FIG. 3, it is apparent that a buiing compound applicator is provided for each of the bufhng wheels, for clarity of illustration, only one buing compound applicator is shown in detail in FIG. 14. Since each of the bufng compound applicators are substantially identical, common reference numerals will be used to indicate corresponding elements on each device.

Referring now to FIG. 14, a wedge of bulng compound 280 is clasped between a laterally extending plate 281, and a laterally extending front plate 282 as `by bolt 283. Rear plate 281 has been bent to form side portion 28M which is pivotally secured as at 284 to a bracket 285. The furthermost rearward ends of portion 281e are bent upwardly as at 28M, `and a latch member 287 is secured thereto as by set screws, not shown. The upper left hand side 287a of latch member 287 provides a latching surface for engagement with other latch means to be described later. Rotation of side portion 281:1 relative to bracket 285 is restricted both in a clockwise and counterclockwise direction by means of a generally U- shaped member 288 xedly attached to bracket 285, having outwardly extending legs 289 and 290. Bracket 285 is rotatably mounted on a pin 291 which is secured in arm 100, and is biased in a counterclockwise direction by tension spring 292 attached to portion 28561. The other end of spring 292 is attached to an outwardly extending arm 293 of a bracket 294 rigidly secured to the turret as at 295.

Also attached to pin 291 is a lever 297 which carries on its lower end, as viewed in FIG. 14, a roller follower 298 in contact with the periphery of cam 215. This contact is maintained by means of tension spring 299 which is connected between the upper portions of lever 297 and an extension 300 of the bearing cap 102.

Lever 297 has attached thereto, as by welding, a transversely extending member 302 adjacent its upper end, and a latch 303 is secured to member 302 by bolt 304. The lower right hand portion 303m of latch 303 is held in `contact with portions 287a of the latch member 287 by the weight of the buffing compound 280 when the device is cocked preparatory to the application of bufling compound, as will be seen hereafter.

Thus, in operation, when the follower 298 begins to ride up on the rise portion of cam 215, lever 297 will begin moving clockwise and the latch 303 aixed thereto will push against latch member 287. This force is transmitted through latch member 287 to pivotal mounting 284 thereby causing bracket 285 and 'bung compound 280 to rotate in xed relation with lever 297. Lever 297 and bracket 285 rotate together until buing compound 280 engages the surface of bufling wheel 93. When the buing compound contacts the bung wheel (which is rotating in the direction shown), the bung wheel reacts against the bufling compound 280 with a normal force F and a friction or drag force D. The sum of these two forces, or the total resultant force of the bufng wheel on the buing compound, is indicated at L and sets up a counterclockwise moment around the pivotal mounting 284. As can be seen by a close examination of FIG. 14, the only resistance to a counterclockwise movement of side 281a relative to bracket 285 about pivotal connection 284 is the friction between the contacting latch surfaces 287a and 303a. This resistive force is overcome by the moment created by force L allowing side 281!) to rotate counterclockwise with respect to bracket 285 thereby causing latch surfaces 287a and 303a to slip out of engagement with each other and at the same time lifting the bufng compound away from the buthng wheel. Since these latch surfaces had been responsible for maintaining the xed angular alignment between lever 297 and bracket 285, there remains no resistive means to prevent counterclockwise rotation of bracket 285 under the bias of spring 292. Bracket 285, therefore, rotates counterclockwise until bumper 306, rigidly axed thereto as at 307, contacts stationary stop 308 on bracket 294. Upperportions of latch member 287 are now disposed to the left of lower portions of latch 303, the latch 303 serving to hold side 281a near its furthermost counterclockwise position with respect to bracket 285 thereby preventing further Contact of the bufling compound with the bufug wheel. It will be understood that bu'ing compound 280 has been out of engagement with bufhng wheel 93 since latch surfaces 287a and 303m slipped out of engagement, and remains out of contact over the entire dwell portion of the cam 215 while the lever 297 is in its furthermost clockwise position.

When the return portion of cam 215 is engaged by roller follower 298, lever 297 rotates counterclockwise under the bias of spring 299 and the lower left hand surface of latch 303 rides up and over latch 287 to cock the device in preparation for the next application of bufling compound. As follower 298 rides up the rise portion of cam 215, the bufling compound 280 is again brought in contact with the bufling wheel and the cycle, as described hereinbefore, is repeated. A stationary cam 215g (FIG. 5) allows compound application only when the bung wheel is in the working position.

We claim:

1. A ball reconditioner comprising in combination: means for supporting a ball in work position; a plurality of ball working devices; a single movable carrier supporting said devices; and means including a single timing member for indexing the carrier to move said ball working devices sequentially into a work position for working upon said ball.

2. A ball reconditioner comprising: a frame having means for rotatably supporting a ball; a plurality of ball working devices; means for sequentially moving said working devices into and out of engagement with the ball; and means for selectively bypassing at least one of said working devices.

3. A ball reconditioner comprising: a main frame; a ball holding frame pivotally mounted on said main frame; guide means on said ball holding frame for rotatably supporting a ball and defining a ball working station; a turret indexably mounted on said main frame and rotatably supporting a plurality of ball working members including a grinding wheel, and at least one buflng wheel; means for indexing said turret to sequentially position said grinding wheel and said bulling wheel at said ball working station; means for pivoting said ball holding frame relative to said main frame as said turret indexes; and means for rotating said ball working members.

4. A ball reconditioner as defined in claim 3 wherein means are provided for rotating said ball.

5. A ball reconditioner as defined in claim 4 wherein means are provided for periodically twisting said ball.

6. A ball reconditioner `as dened in claim 3 wherein said `grinding wheel has an arcuate surface adapted to engage said ball.

7. A ball reconditioner as dened in claim 6 wherein means are provided for periodically dressing said grinding wheel to maintain said Iarcuate surface.

8. A ball reconditioner as defined in claim 3 wherein means are provided for periodically applying buffing compound to said buffing wheel.

9. A ball reconditioner as defined in claim 3 wherein means are provided for lifting the ball from the ball holding frame at the end of the reconditioning cycle.

10. A ball reconditioner as defined in claim 9 wherein the means for indexing the turret include a Geneva mechanism with a step corresponding to each of the ball working members, and with a intermediate step between each of said first mentioned ste-ps.

11. In a ball reconditioning machine having a plurality of ball working members adapted to be moved sequentially into engagement with a ball, a timing device for controlling the movement of the ball working members comprising: a driven input shaft; a single timing disc continuously rotated by said shaft; a follower adapted to ride upon said disc; means on said disc for periodically moving said follower; and means operable in response to movement of said follower for moving said ball working members.

12. In a ball reconditioning machine having a reconditioning cycle consisting of the steps of grinding, rough bufiing, and finish buffing, performed by a grinding wheel, and first and second bufling Wheels respectively, a timing device for controlling the sequential operation comprising: a constantly rotating cam having a plurality of spaced actuators; a cam follower adapted to ride along said cam and engage said actuators; an output uneinber adapted yto lrnove said grinding Wheel, said first bufiing Wheel and said second buffing wheel sequentially into engagement with said ball; and clutch means operable in response to the engagement of said follower with an actuator to drive said output member.

13. A timing device for controlling the shifting of the ball working members in a ball reconditioning machine having a plurality of ball working members cornprising: a housing; a timer disc in said housing and having peripherally spaced actuators; the peripheral space between said actuators corresponding to the ball working operations and said actuators corresponding to a shift between the ball working members; means for rotating said disc at a predetermined speed; a follower movably mounted in said housing and adapted to ride along the periphery of said disc; a clutch having an input member, and an output member adapted to shift said ball working members; means for rotating said input member at a speed substantially in excess of the speed of said disc; latch means associated with said follower for connecting said clutch output member with said clutch input member when said follower engages an actuator to effect a shift in said ball working members; and means for releasing said clutch output member from said clutch input member when said follower is out of engagement with an actuator.

14. In a ball reconditioner with a turret having first, second, and third ball working members, an actuator for use in a timing device that controls the sequential movement of the ball working members comprising: a disc having substantially identically shaped halves; the outer periphery of each half having a first actuator adapted to shift the turret from a position between said third working member and said first working member to said first working member; a second actuator positioned immediately adjacent said rst actuator and having a length substantially twice as long as said first actuator and adapted to immediately shift said turret from said first working member to said second working member; a first peripheral surface adjacent said second actuator and having a length substantially longer than either `of said actuators and corresponding to the duration of the operation of said second ball working member; a third actuator adjacent the end of said first peripheral surface and having a length corresponding to the length of said second actuator and adapted Ito shift said turret from said second working member to said third working member; a second peripheral surface adjacent said third actuator and having a length corresponding to the duration of the operation of said third ball working member; and a fourth actuator adjacent the end of said second yperipheral surface and having a length substantially corresponding to the length of said first actuator to shift said turret from the third working member to a position intermediate said third working member and said first working member.

15. In a ball reconditioning device including a turret rotatably supporting a grinding wheel and first and second buffing wheels, and having a first reconditioning cycle including first and second buffing operations, and a second reconditioning cycle including a grinding operation, and first and second buffing operations, a timing device for controlling the sequential movement of the ball working wheels into engagement with the ball cornprising: a housing; a timing disc mounted in said housing and having substantially identically shaped halves, one of said halves being adapted to control the first cycle, and both of the halves being adapted to control the second cycle; means for rotating said disc, means for selecting said first or second cycle; each of said disc halves including a plurality of spaced actuators; a follower movably mounted in said housing and adapted to ride upon said disc; `a clutch having an input member, and an output member adapted to shift said ball working tools; means for rotating said input member at a speed substantially in excess of the speed of said disc; latch means associated with said follower for connecting said clutch output member with said clutch input member when said follower engages an actuator to effect a shift in said ball working tool; means for releasing said clutch output member from said clutch input member when said follower is out of engagement with an actuator; each of said halves having a first actuator adapted to shift the turret from a position intermediate said second buffing wheel :and said grinding wheel to said .grinding wheel; a second actuator positioned immediately adjacent said first actuator and having a length substantially twice as long as said first actuator and adapted to immediately shift said turret from said grinding wheel to said first buffing wheel; a first peripheral surface adjacent said second actuator and having a length substantially longer than either of said actuators and corresponding to the duration of the first bufiing operation; a third actuator adjacent the end of said first peripheral surface and having a length corresponding to the length of said second actuator and adapted to shi'ft said turret from said first buing Wheel to said second bufiing Wheel; a second peripheral surface adjacent said third actuator and having a length corresponding to the duration of the operation of said second bufii'ng wheel; a fourth actuator adjacent the end of said second peripheral surface and having a length substantially corresponding to the length of said first actuator to shift said turret from said sec-ond buffing wheel to a position intermediate said second biiffing wheel and `said grinding wheel; latch means for holding said follower out of engagement with `said disc during the first hal-f revoltuti-on -of the disc in the `second cycle whereby said turret does not index Aimmediately to said buffin-g wheel; and means -for releasing said latch means at the end of said half revolution.

16. A ball reconditioner as defined in claim 15 wherein said follower includes an extension, and wherein said latch means includes a latch body pivotally mounted in said housing and movable into engagement with said follower when said second cycle is selected.

17. A ball reconditioner as defined in claim 16 wherein said means for releasing said latch means includes a pair of release members pivotally mounted on said disc at diametrically opposed positions, and wherein said latch body includes a portion positioned inthe path of travel of said release members that is engageable with a release member upon rotation of said disc.

18. A ball reconditioner as defined in claim 15 Wherein said means for rotating said disc includes a planetary gear train.

19. In a device for grinding a spherical object, the combination of: a support; a grinding Wheel rotatably mounted on said support and having an arcuate grinding surface adapted to engage said object; ymeans for rotating said grinding wheel; a dressing device mounted adjacent said grinding wheel for periodic movement across .said surface; `an Iactuating member pivotally trnounted on said support; linkage means connecting said actuating member and said dressing device; and means for periodically lpivoting said `actuating member to move said dressing device across said surface.

20. In a device for butiinlg a spherical object, the combination of: a support; a buiiing Wheel rotatably mounted on said support and adapted to engage said object; means for rotating said buing wheel; a bufng compound applicator mounted for movement toward and away from said wheel; an actuating member pivotally mounted on said support and engaging said applicator; means for pivoting said actuating member to move said applicator towards said wheel; and imeans `oper-able `in response to the engagement of said applicator with said Wheel for moving said applicator away from said wheel.

21. The method of reconditioning a bowling ball cornprising the steps of placing a ball at a ball working station, moving a `grinding tool into .a working position adjacent said ball, grinding a predetermined amount of stock from the outer surface of said ball, simultaneously moving said grinding tool out of the Working position and moving a first buffing tool into the Working position, bufng the outer surface of said ball with said iirst buing tool to remove the marks caused by said grinding tool, simultaneously moving said first bufling tool out of the Working position and moving a second buing tool into the moving position, and bufiing the outer ,surface of the ball with said second .buiiing tool to polish the outer surface of said ball.

22. In a ball reconditioning machine, the combination of: means including at least two tools for providing two ball reconditioning and treating cycles, the iirst of said cycles including a grinding operation and the second of said cycles excluding a grinding operation; a grinding wheel having an Iarc-uate :grinding surface 'for performing said grinding operation during said first cycle; means for rotating said grinding wheel; a dressing device for engaging said grinding surface; means for swinging said dressing device in an arc corresponding to the `grinding surface to dress said sur-face during said first cycle; and means for precluding operation -of .said swinging means during said second cycle.

23. A device for applying buffing compounds to a buiiing wheel comprising: a buing compound holder mounted adja-cet a lbuiiing wheel for periodic movement toward and away from said Wheel; means for moving said holder toward said wheel; .and means responsive to the engagement of said holder with said wheel for moving said holder away from said wheel.

References Cited by the Examiner UNITED STATES PATENTS 334,296 1/1886 Smith 51-263 888,675 5/1908 Ward et al. 125-11 1,754,630 4/1930 Klamp et al. 125-11 1,842,551 1/1932 Klos 51--166 X 2,006,953 7/1935 Klos 5143 X 2,156,562 5/1939 Cramer 125--11 2,321,162 6/1943 Sohlm 15-21 2,366,623 1/1945 Jakobsen 12S-11 2,588,714 3/1952 Fleming 51-4 2,619,662 12/1952 Hayes et al. 15-21 2,733,464 2/1956 Le Mieux 15-21 3,016,553 1/1962 Wilhelm et al 51-289 X FOREIGN PATENTS 538,876 4/1957 Canada.

LESTER M. SWINGLE, Primary Examiner. 

1. A BALL RECONDITIONER COMPRISING IN COMBINATION: MEANS FOR SUPPORTING A BALL IN WORK POSITION; A PLURALITY OF BALL WORKING DEVICES; A SINGLE MOVABLE CARRIED SUPPORTING SAID DEVICES; AND MEANS INCLUDING A SINGLE TIMING MEMBER FOR INDEXING THE CARRIER TO MOVE SAID BALL WORKING DEVICES SEQUENTIALLY INTO A WORK POSITION FOR WORKING UPON SAID BALL. 